Rotary piston pump with dual chambers



April 18, 1967 Q A. J. JACOBS- 3,314,370

ROTARY P ISTON PUMP WITH DUAL CHAMBERS v 6 Sheets-,Sheetl Filed March 16, 1964 Albert J Jacobs INVENTOR,

April 18, 1967 A. JQJACOBS 3,314,370

ROTARY PISTON PUMP WITH DUAL CHAMBERS Filed March 16, 1964 6 Sheets-Sheet 2 13:29:? I $11 20 Fig. 2 I! Albert J Jacobs INVENTOR.

BY Q April 18, 1967 A. J. JACOBS 3,314,370

ROTARY PISTON PUMP WITH DUAL CHAMBERS 7 Filed March 16, 1964 a Sheets-Shed :s

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' ROTARY PISTON PUMP WITH DUAL CHAMBERS Filed March 16, 1964 6 sheets-sheet 5 Fig. 6

A/berf J1 Jacobs INVENTOR.

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ROTARY PISTON PUMP WITH DUAL CHAMBERS Filed March 16, 1964 6 Sheets-Sheet s Fig. /6

Fig. /4 /74 United States Patent 3,314,370 ROTARY PISTON PUMP WITH DUAL CHAMBERS Albert J. Jacobs, Calgary, Alberta, Canada, assignor to Edward J. Carline, Edmonton, Alberta, Canada Filed Mar. 16, 1964, Ser. No. 352,206 16 Claims. (Cl. 103-132) This invention comprises a novel and useful rotary piston pump with dual chambers and generally pertains to the rotary piston positive displacement type of an expansible chamber device capable of use as a pump, fluid motor, external or internal combustion engine, steam engine and the like.

It is the primary object of this invention to provide a rotary piston expansible chamber device capable of efficient operation as a pump, engine or fluid pressure motor.

A very important object is to provide a device in accordance with the foregoing object which shall be capable of operation under extremely high internal pressures and temperatures. H

Another important object is to provide a device in conformity with the preceding objects which shall be extremely compact and of simple construction, durable and of low cost.

Yet another object is to provide a device in compliance with the above-mentioned objects wherein a plurality of expansible chamber units, each unit including radial inner and outer working chambers compactly disposed in axial alinement in a single housing and connected to a single power shaft.

An additional object is to provide a multiple unit device wherein the units are so connected to a common drive shaft as to balance the peak pressures and pulsations of the units and obtain a substantially even flow of power into or out of the device.

A further object is to provide a multiple unit device having connected fluid inlet and fluid outlet means for the plural units, so arranged as to minimize pressure pulsations and flow of fluids.

An additional object is to provide an expansible chamber device of the rotary piston, positive displacement type in which the volume of the working chambers shall comprise as large a proportion of the total volume of the device as possible.

Still another object is to provide a construction having an improved wear plate and sealing plate construction which shall be self-adjusting and shall be pressure loaded by the fluid being handled by the device A further object is to provide a compensating sealing means between the moving surfaces of the piston and the working chamber Walls which shall automatically take up any clearance therebetween arising from wear, temperature, inaccuracies in the fit of the parts and other causes and which shall be operable to exert a clearance take up force in response to an operating pressure of fluid supplied to the device.

Another object is to provide a compensating sealing construction according to the immediately preceding object wherein rings are provided to function both as sealing means and as replaceable wear elements and which shall be sufliciently flexible to establish a fluid tight seal between the piston and chamber side walls despite irregularities in the engaging surfaces and shall distribute the fluid pressure applied to the sealing uniformly over the contacting surface of the adjacent piston, thereby reducing the necessity for precision machining of surfaces and alinement of parts.

An additional object is to provide a pressure urged, compensating sealing means wherein the compensating pressure applied thereto is derived from pressure in the working chamber of the device.

. 3,314,370 Patented Apr. 18, 1967 Still another object is to provide in a device of the character described sealing means between various relatively moving surfaces which shall be actuated in response to and by the pressure in the working chambers to urge the sealing means into sealing engagement by fluid pressure forces derived from the working chamber pressures.

An additional object is to devise an expansible chamber device of the rotary piston type replacing substantially all reciprocating movements with continuous uni-directional rotation or translation movements and wherein a ring-like piston is mounted for translation movement within a cylindrical chamber while maintaining tangency with cylindrical concentric internal and external surfaces thereby providing inner and outer working chambers for said piston in each unit.

Another object is to provide a device as in the immediately preceding object which shall have a controlling and stabilizing means connected to the stator and rotor and limiting the latter to translational movement in an orbit and shall be equally capable of withstanding heavy loads in either direction.

Yet another purpose of the invention is to provide an apparatus in conformity with the immediately preceding object wherein the controlling and stabilizing device shall be compactly mounted within a recess in the end walls of the stator of the apparatus.

A very important object of the invention is to provide a rotary piston device which utilizes a translatory moving of a ring piston about a central core and within a stator chamber to minimize movement between working parts subjected to sliding friction, to reduce wear, to minimize bearing loads, peak pressures, centrifugal forces and the velocity of moving parts relative to each other.

Another very important object is to provide a simple, compact but positive driving connection between a ring piston and a stator which will confine the piston to translatory movement in an orbit about a central axis and wherein said connection shall function as a liquid circulating or impelling means for a lubricating and cooling medium within the device.

Still another important object is to provide a connecting means of a planetary gear type wherein the forces and backlash of the connecting means aresimultaneously distributed over a plurality of engaging gear teeth and recesses or pockets.

Yet another purpose of the invention is to provide a device as set forth in the preceding objects which shall have a simplified but highly advantageous piston construction wherein the ring piston has side plates which support the latter for movement and which embrace therebetween a central core member of the apparatus.

A still further object of the invention in compliance with the immediately preceding object is to provide a cooperating piston and core construction wherein the latter is provided with a plurality of circumferentially spaced axial bores and whereby brace rods under tension and spacer sleeves under compression connect the side plates of the piston and are received each within one of the bore-s of the stator.

Another auxiliary object is to provide rollers journaled upon the spacer sleeves and having each in rolling contact within the inner peripheral surface of the associated core axial bores.

An additional important object is to provide a construction wherein various components are mounted upon a centrally disposed drive shaft and are slidably displaceab-le axially thereon by a pressure operated wear and clearance compensating for taking up slack therebetween, the shaft being fixedly secured in one end component but being relatively axially slidable in the other components and other end component.

An important object is to provide :a novel and highly eflicient radially extending partitioning blade for each of the inner and outer working chambers of an exp-ansible chamber device of the positive displacement ring pistontype which shall have its sealing pressures varied in accordance with the working pressures of the device.

An important object is to provide a novel and highly efiicient radially extending partitioning blade for each of the inner and outer working chambers of an expansible chamber device of the positive displacement ring pistontype which shall have its sealing pressures varied in accordance with the working pressures of the device.

Another subordinate object is to provide inner and outer partitioning blade assemblies which shall eifectively employ pressure differential areas upon their opposite ends for obtaining a resultant sealing pressure dependent upon the working chamber pressures.

Yet another object is to provide a partitioning blade assembly wherein the sealing pressure applied to differential areas thereof shall be supplemented by a mechanically applied sealing force.

Still another object is to provide a partitioning blade construction for the outlet working chamber which shall be pressure urged continuously into a sealing engagement which continuously functions as an exhaust port means for the inner working chamber.

These together with other objects and advantages which will become subsequently apparent reside in the details of construction and operation as more fully hereinafter described and claimed, reference being had to the accompanying drawings forming a part hereof, wherein like numerals refer to like parts throughout, and in which:

FIGURE 1 is a side elevational view of a suitable form of an apparatus of the dual chamber type incorporating therein the principles of this invention;

FIGURE 2 is a view in vertical transverse section taken upon an enlarged scale substantially upon the plane in dicated by the broken section line 2-2 of FIGURE 1 and. showing the internal construction of one of the dual chamber units of the invention, parts being shown in elevation and other parts in section;

FIGURE 3 is a view in vertical longitudinal section taken substantially upon the plane indicated by the broken section line 33 of FIGURE 2 and showing the internal structure and relative position of the piston units of the two dual chambers of this form of the invention.

FIGURE 4 is a view in vertical transverse section taken substantially upon the plane indicated by the section line 44 of FIGURE 3 and showing one of the controllin and stabilizing units of the invention;

FIGURE 5 is an exploded perspective view of the two cooperating members or elements of a controlling and stabilizing unit, parts being broken away;

FIGURE 6 is a detail view taken upon an enlarged scale in vertical longitudinal section substantially upon the plane indicated by the broken section line 6-6 of FIGURE 2 and showing certain details of the core, core journal and inner partitioning blade of the invention;

FIGURE 7 is a detail view in vertical transverse section taken substantially upon the plane indicated by the section line 7-7 of FIGURE 6;

FIGURES 8-11 are diagrammatic views showing in sequence successive positions of one of the ring pistons throughout one complete cycle of operation of the latter;

FIGURE 12 is a detail view showing upon an enlarged scale a sealing means employed with the inner partitioning blade;

FIGURE 13 is a perspective view of the inner partitioning blade;

FIGURE 14 is a detail view in vertical transverse section of the outer partitioning blade assembly;

FIGURE 15 is a detail view in vertical transverse section taken substantially upon the plane indicated by the section line 1515 of FIGURE 14; and

FIGURE 16 is an exploded perspective view of a por- 4 tion of the outer partitioning blade of FIGURE 14 and of the sealing sleeve thereof.

General construction In the following specification, the principles of this invention have been illustrated and described specifically as being embodied in a fluid pump. It will be understood, however, that with obvious changes in the necessary accessory equipment, the same expansible chamber device disclosed in the pump embodiment can likewise be employed as a fluid pressure operated motor, an internal combustion or external engine, a steam engine or the like.

The numeral 10 designates generally the dual chamber unit embodiment of this invention which comprises a cylindrical stator or housing indicated generally by the numeral 12. As will 'be seen by reference to FIGURES l and 3, the stator is composed of a number of separate sections detachably but rigidly secured together. Thus, there is provided a pair of cylindrical rims shown at 16 and 18 with a circular partition in the form of a plate 19 interposed therebetween. A pair of end plates 20 and 22 provide closures for the opposite ends of the hollow cylindrical casing, and these parts are united detachably as by means of through bolts 24.

With continuing reference to FIGURE 3, it will be seen that each of the end walls has an axially outwardly projecting hollow portion shown at 26 for the end wall 20 and at 28 for the end wall 22. The projecting portion 26 has an annular chamber 30 disposed therein while a similar chamber 32 is provided for the portion 28. Centrally of the end walls there are provided inwardly projecting bosses 34- :and 36 respectively in which are received bearing assemblies 38 and 40 retained by end caps 46 and having retaining bolts 48 and 52. The cap 46 has therein a bearing sealing member 42. The cap 50 has an inwardly projecting flange 54 which abuts against the bearing assembly 40 and also encloses a bearing retainer 44 which is detachably secured to a shaft 58 by means of fastening bolts 56.

It will be observed that the power shaft 58 is disposed centrally through the sections and the central hollow therein, the shaft being journaled in the bearings 38 and 40 and having a central splined portion 60. One end of the shaft, carrying the bearing retainer 44, terminates within the stator while the other end projects through the end wall 26 and the closure cap 46 and is connected to a suitable source of power, not shown, when the device is to operate as a pump or serves as a power take-01f means when the device becomes a prime mover such as a fiuid pressure motor or engine.

Slidably secured to the splined portion 60 of the shaft for rotation therewith are a pair of rotor hubs or journals in the form of'discs or drums each indicated by the numeral 62, one such hub being disposed in the cylindrical chamber between the partition 19 and an end wall 20 and the other being disposed in the chamber between the partition 19 and the end wall 22. Rotatably mounted. upon each of the cylindrical journals or hubs 62 as by means of a cylindrical bushing 64 is a cylindrical core in the form of a disk or drum 66.

Referring now to FIGURE 3 it will be understood that each of the chamber units of the apparatus is identical, and each has a cylindrical chamber therein defined by the cylindrical inner peripheral wall of the stator or casing section 16 or 18 and the cylindrical outer wall of the core 66. These cylindrical walls are identified at 68 and 70 respectively and comprise the radial outer and inner boundaries of the cylindrical chambers whose side walls are each defined by an end plate 20 or 22 and the partition plate 19.

Each of the cylindrical chambers receives a ring-like piston therein designated generally by the numeral 72. Since the ring pistons are of identical construction, the same reference numerals will be employed to designate the same component element of each. Referring primarily to FIGURE 3 it will be seen that each of the ring pistons comprises a cylindrical peripheral rim element 74 having a pair of end walls 76 and 78 which engage the peripheral edges of the rim 74 and support the latter. The end walls 76 and 78 comprise support plates for the piston and are provided with central openings each indicated by the numeral 80. Also axially and slidably secured upon the splined portion 60 of the drive shaft 58 are pairs of eccentric support members 82 of identical construction, which by means of bearing assemblies 84 upon their peripheries are received within counterbores or recesses within the openings 80 to rotatably support the support plates 76 and 78 about an eccentric axis offset from the rotational axis of the shaft 58. In this manner, the ring pistons are mounted for displacement and translatory movement about an eccentric support means fixed to and carried rotatably by the shaft 58, thereby disposing the pistons for movement eccentrically each within one of the cylindrical chambers of the two housing sections. The eccentrics 82 are preferable axially bored at 83 to lighten their weight and also to enable passage of oil therethrough for cooling and lubricating purposes.

The support means and the ring pistons are of such size and so proportioned that the ring pistons are continuously tangent to both the peripheral cylinder surface 68 of the stator unit and the cylindrical exterior surface 70 of each associated core 66, this relation being shown clearly in FIGURE 2 and being diagrammatically indicated in the diagrammatic views of FIGURES 8l1.

At this point it should be noted that at least one of the support plates 76 and 78 is removably but rigidly secured to the rim 74 of its associated piston as by fasteners 79 thereby providing means for readily assembling and disassembling the pistons in position in the apparatus.

Because of the tangencies of each ring piston in its cylindrical chamber, the latter is divided into radially outer and inner working chambers as indicated at 86 and 88 respectively, FIGURE 2. The outer chamber 86 lies between the ring piston 72 and the peripheral cylinder wall 68, while the inner chamber 88 lies between the inner surface of the ring piston 72 and the core surface 70.

In a manner to be subsequently set forth, the piston is caused to have a translational movement only with respect to the core and the stator, as indicated by the diagrammatic views of FIGURES 8-11 so as to cause a progressive movement of outer and inner working chambers about the circumference of the ring piston and the associated surfaces of the core and stator.

Referring again to FIGURE 3, it will be seen that suitable annular positioning and aligning rings as at 90 are interposed between the machined, planar mating surfaces, in suitable complementary circumferentially extending channels or grooves of the elements 19, 16 and 18 and 20 and 22. Further, an oil level filling plug is indicated at 92 in the bearing cover plate 50.

Compensating sealing plates A replaceable and automatically adjustable or compensating combined sealing ring and wear plate assembly is provided for each of the cylinder units of the apparatus. These sealing plates take up any axial clearance and axially urge the components into close fitting engagement. Thus, referring still to FIGURE 3, each of the end walls 20 and 22 has its inner surface provided with a circumferentially extending recessed channel or groove as at 94 and 96 respectively while the opposite sides of the partition 19 are similarly provided with complementary channels or grooves -at 98 and 100. Secured in the recesses 94 and 96 of the two end plates in a removable manner as by the fastening bolts 102, are identical annular sealing rings and wear plates 104. It will be observed that the inner surfaces of these plates are substantially flush with the inner surface of the corresponding end plates 20 and 22. In a similar manner, a pair of identical movable sealing and wear plates 106 are disposed in the recesses 98 and 100 of the partition plate but with their adjacent rear surfaces being placed in communication with each other by means of bores or passages 108 extending through the partition therebetween. The movable sealing plates 106 are recessed upon their back sides to provide channels which with the cross bores 108 are filled with an incompressible pressure transmitting liquid such as oil or grease constituting an operating fluid for the compensating plates 106. The operating fluid under pressure from any suitable source is supplied through a suitable bore 109 in the partition 19 as shown by dotted line in FIGURE 3 to the passage 108 in any suitable manner so as to thereby exert a fluid pressure force on the movable wear plates 106 to urge them towards the stationary compensating seating plates 104. It will be observed that the piston side plates 76 and 78 are in sliding engagement with the corresponding pair of sealing and wear plates 104 and 106 so as to establish a fluid-tight seal therewith. The inner and outer diameters of the sealing plates 104 and 106 are also dimensioned as shown in FIGURE 3 to only cover the annular chamber within which the working spaces 86 and 88 are formed in order to limit wear on the working chamber walls. These plates are thus also readily replaceable and self-compensating for wear under the fluid pressure imposed thereon.

The pressure compensating sealing plates 106 take up all axial slack between the components 20, 82, 62, 72 and 104. For this purpose the shaft 58 is fixedly axially secured in the end wall 28 but is axially slidable in the end wall 26 while each of the components 82 and 62 is axially shiftable upon the shaft.

It will be seen from FIGURE 3 that the compensating sealing plates 106 are provided with channels and sealing rings 107 upon their outer peripheral edges while the partition recess 98, 100 have sealing rings and channels 113 engaging the inner peripheries of the plates 106. These rings 107 and 113 may likewise be supplied with fluid pressure as from the bore 109 through passages 108.

Core and piston Referring now to FIGURES 2, 3 and 7, it will be observed that the core 66 has a plurality of circumferentially spaced axially extending bores or passages therethrough. Brace rods or reinforcing elements are provided comprising tension bolts 122, each of which extends through one of the bores 120 and is secured under tension to the two support plates 76 and 78 of each piston. Spacer bushings 124 surround each of the brace rods or tension members 122, these bushings being disposed and movable within the core bores 120 with their ends placed under compression by engagement with the adjacent support or side plates 76 and 78. By these means, axial compression is applied to the support plates thus rendering the piston assembly of sturdier construction and with the spacer sleeves and rollers thus being disposed for movement within the bores 120 as shown in FIGURES 2, 3 and 7. In this manner, a very compact structure is provided which greatly strengthens the rigidity and structural strength of the piston and by disposing the reinforcing members within the confines of the core itself, the overall radial dimensions of the device are likewise reduced. Freely rotatably journaled upon each spacer sleeve 124 and between the piston side plates 76 and 78 is a roller 125 which continuously rotates about the inner surface of its bore 120. This engagement maintains the core against rotation.

bilizer and piston control construction which maintains the ring pistons in parallel positions throughout their gyratory or orbital movement and confines them to a translational motion. In the dual unit construction of FIGURES 1-11, two such stabilizers are provided, one being disposed at each end of the stator. Referring now to FIGURE 3 in conjunction with FIGURES 4 and 5, it should be understood that each control stabilizer construction or assembly consists of a pair of cooperating members or elements comprising an internal ring gear 126 and an external ring gear 128 cooperating therewith. The internal ring gear is received Within the chambers 30, 32 of the two stator end plate cover members 26 and 28, being detachably secured in place as by suitable fastener bolts 130. A cooperating element or member consisting of the external ring gear 128 is secured as by fastening bolts 132 to the support plate 78 at the outer side of the ring piston assembly. Thus, the internal ring gear member 126 is maintained stationary by being fixedly secured to the stator while the external ring gear member 128 is fixedly secured to and moves with the corresponding ring piston assembly.

Referring more particularly to FIGURES 4 and 5, it will be noted that the internal ring gear member 126 is L-shaped in cross section having a mounting flange 134 thereon together with a cylindrical skirt or rim portion 136. Radially inwardly projecting teeth 138 are provided upon this rim defining cylindrical shaped open pockets 140 therebetween. The teeth between the pockets are provided with apertures or bores at at 142 for the recept-ion of the previously mentioned fastening bolts 138.

In a similar manner, the external ring gear 128 or inner member of the stabilizer or control assembly likewise is L-shaped in cross section as will be apparent from FIGURE 3, including an annular flange 144 together with the cylindrical flange or rim 146. Apertures as at 148 through the flange 144 serve to receive the fastening bolts 132 previously mentioned. Projecting radially outwardly from the outer periphery of the cylindrical flange 146 are a plurality of teeth 158. It will be observed from FIGURE 4 that there is provided one such tooth 150 for each pocket or socket 140 of the internal ring gear mem ber. As shown by the arrows in FIGURE 4, the proportions are such that during the translational or gyratory movement of the ring piston and the external ring gear member attached thereto, these teeth will have a circular motion causing them to enter into and travel about the corresponding pocket or recess 140. By virtue of this engagement, although the external ring gear member had a gyratory motion, it is restrained against turning about its own central axis and thus is given a purely translational motion. In this manner, the ring pistons are maintained in a parallel position throughout their gyratory or orbital path of travel thereby serving to precisely time the orbital path of travel of the tangency of the ring piston with both the stator and core elements of the apparatus.

Partitioning blade assemblies There are provided radially inner and outer partitioning blade-s 152 and 154 respectively extending radial-1y across the inner and outer working chambers 88 and 86, see FIG- URES 2, 6 and 7. These blades constitute dividing partitions for the inner and outer working chambers 88 and 86 and establish asealing engagement with the inner surfaces respectively of the ring piston 72 and the inner surface 68 of the stator. Both blades are of a generally rectangular, plate-like configuration.

The inner partitioning blade 152 is slidably received in a radial slot 159 in the core 66. An actuating stem 156 extends inwardly from the blade 152 and is slidably guided in a bore 160 extending through the core 66, which bore communicates with the bottom portion of the slot 159. A cam groove 164 extends circumferentially about the core journal 62 and receives therein a T-shaped shoe 158 which a-ctuatingly engages the inner end of the stem 156 which extends through a corresponding opening in thecore bushing 64. The proportions are such that the 8 cam groove 164 and foot 158 will maintain the radially outer edge of the blade 152 substantially in sealing en gagement with the internal surface of the ring piston 72.

In its lower end, the bore 160 has an enlarged counterbore 162 in which is press-fitted a cylindrical bushing 161 as more clearly shown in FIGURE 12 functioning as both a stem guide and a pressure seal retainen. The bushing is internally grooved to receive an O-ring seal 163 which slidably embraces the stem 156. Access is bad to each counterbore 16-2 by a bore 165 extending into the slot 159 to permit passage of a knock-out tool when it is desired to remove the bushing 16-1.

As shown in FIGURE 13, the inner partitioning blade 152 has two parallel grooves 153 upon its face which is exposed to the high pressure side of the inner working chamber 88, conducting the pressure to the underside of the blade 152. Since the upper edge of the blade is semicylindrical or convex, only half of the cross sectional area of the top of the blade is exposed to the high pressure while all of the area at the bottom is exposed. Thus there is a differential area and pressure effect urging the inner blade radially outwardly into a pressured sealing engagement with the inner surface of the ring piston 72. This fluid pressure biasing effect is always dependent upon the regulated working pressure of the high pressure side of the inner chamber 88.

The previously mentioned bushing 161 and its O-ring 163 prevents the escape of this pressure into the central portion of the casing.

The outer partitioning blade assembly 154 serves both as a partition for the outer working chamber 86 and as a part of the exhaust system for the inner working chamber 88. It includes a radially and upwardly extending slot, recess or chamber 168 formed in the stator and opening upwardly from the stator inner surface 68 of the outer working chamber 86. At its outer end, the 'slot has a blind bore 170.

Slidable in the slot 168 is the outer partitioning blade 154 which is a hollow box-like member 180 open at its top and having a bottom wall 181. A spring retainer plate 174 is seated in the upper end of the slot 168 and has a depending valve stem guide sleeve 175 which receives the Valve stem 172 slidable therethrough and into the bore 170. At its lower end, the valve stem carries a poppet valve head 184 cooperating with a valve seat 182 at the upper end of the exhaust port 183 in the bottom wall 181. An inner valve spring 178 surrounds and is guided by the member 175 and abuts against the plate 174 and the valve head 184. An outer spring 176 is received within the guide sleeve 177 having an intumed flange 179 at its upper end which is retained against the retainer plate 174, the lower end of the sleeve 177 being open and the lower end of the outer spring engaging the bottom wall 181 to urge the member of the partitioning blade assembly inwardly of its slot 168 and towards the ring piston 72.

It will be observed that openings 185 in the sleeve 177 and 186 in the body 180 are registerable and establish communication between the interior of the outer blade assembly and the exhaust passage 188 in the stator which communicates with the exhaust manifold 190. 7

The lower surface of the bottom wall 181 of the blade or body 180' is provided with a transversely extending semi-cylindrical recess or channel 191, communicating with the port 183, and in which is rockably received a sealing element or shoe 192. The upper portion of the shoe 192 is transversely convex for rocking movement in the seat or recess 191. One or more openings or passages 194 extend through the shoe 192.

Upon its bottom surface, the shoe 192 is transversely concave and is contoured to have a fluid tight seating engagement with the exterior surface of the ring piston 72. As shown in FIGURES 2 and 14, the concave bottom surface of the shoe 192 is inwardly recessed at 195 to provide a clearance space or exhaust collection chamber which is continuously in communication with the passage 194. Additional recesses 197 in the shoe bottom surface on opposite sides of the chamber 195 receive retaining blocks 201 secured by screws 199 whereby the shoe 192 is rockably secured to the blade 154.

It is to be noted that the sealing shoe 192, see FIG- URE 2, is offset from the center of the partitioning blade 154 towardsthe high pressure side thereof, and the valve 184 and the valve stem, seat and port are likewise offset. This insures a greater area on top of the shoe 192 exposed to the high pressure side of the outer chamber than is exposed to the low pressure side obtaining a pressure differential which aids the spring 176 in urging the shoe into sealing engagement with the ring piston 72. This pressure biasing of the sealing shoe is proportional to the working pressure in the outlet chamber.

The ring piston 72 has an exhaust port or passage 196 therethrough which is continuously in registration with the chamber 195 in the sealing shoe and then with the exhaust passage 188. During the translational movement of the ring piston 72, the lower rectangular sealing edges of the shoe 192 continuously enclose the piston exhaust passage 196 of the inner working chamber while maintaining a sealed engagement with the external surface of the ring piston.

An important feature of the above set forth construction is that a differential pressure action is obtained which urges the sealing shoe into engagement with the ring piston 72. Thus the area beneath the shoe which is exposed to the exhaust pressure within the inner chamber is considerably less than the cross sectional area of the top of the blade 154. Therefore when the valve 184 opens, the exhaust pressure applied to the top of the blade 154 and shoe 192 is greater than the pressure applied to the underside of the shoe, thereby producing a resultant pressure difference retaining the shoe in sealing engagement with the ring piston.

The outer working chamber 86 is exhausted through the stator by means of the exhaust passage 198 in the stator which communicates with the exhaust manifold 190 under the control of an exhaust valve 200 of the poppet type which is spring-closed as by the valve spring 202, a combined spring retainer and valve stem guide 204 being provided in the form of a sleeve encircling the valve stem and having a flanged extremity as at 206 against which the valve spring abuts. The guide 204 is axially alined with the valve seat and the flange 206 is clamped in position by the exhaust manifold 190.

In order to provide for the intake of fluid into the inner and outer annular working chambers, there is provided an intake manifold 210 communicating with an intake passage 212 in the stator. This passage in turn is continuously in communication with the outer Working chamber 86. During the gyratory movement of the ring piston, an intake port 214 of the latter is registrable with the passage 212 to admit the flow of fluid from the intake manifold through the ring piston and into the inner working chamber 88 as shown in FIGURE 2.

Thus, means are provided for the automatic and synchronized intake of fluid and the exhaust of fluid from the two working chambers of the device.

From a consideration of FIGURES 8-11, it will be noted that the gyratory motion of the ring piston 72 causes its points of'tangency with the cylindrical surface of the stator and the cylindrical surface of the core to progress circumferentially thereabout whereby the two working chambers provide on opposite sides of the ring piston will likewise travel progressively about the core. During this travel, the ring piston will cooperate with the intake and exhaust passages in the stator for the purpose of directing and controlling the inlet and exhaust of fluid into and out of the two working chambers in a manner which will be readily apparent.

It will be understood that the apparatus may be mounted or supported in any suitable environment in any desired manner. As shown in FIGURE 2, the mounting flanges 220 may be provided upon the stator for this purpose.

The foregoing is considered as illustrative only of the principles of the invention. Further, since numerous modifications and changes will readily occur to those skilled in the art, it is not desired to limit the invention to the exact construction and operation shown and described, and accordingly all suitable modifications and equivalents may be resorted to, falling within the scope of the invention as claimed.

What is claimed as new is as follows:

1. A rotary piston expansible chamber device comprising a stator having a chamber therein including a peripheral wall and a pair of annular side walls, a core disposed within said chamber, a ring piston in said chamber having sides slidingly engaging said side walls and dividing said chamber into radially spaced outer and inner working chambers disposed respectively adjacent said peripheral wall and said core, a shaft rotatably journaled coaxially in said chamber, a hub fixed to said shaft rotatably mounting said core concentric to said chamber, eccentric support means fixedly secured to and rotatable with said shaft and supporting and maintaining said ring piston tangent to said core and said peripheral wall, stabilizing means including a pair of cooperating interengaged members fixedly secured one to said stator and the other to said ring piston and confining the latter to translational movement about said core, intake means supplying a fluid to each of said inner and outer working chambers, exhaust means discharging fluid from each of said inner and outer working chambers, said ring piston comprising a cylindrical rim and a pair of support plates each secured to said rim and journaled upon said eccentrio support means, said core having a plurality of circumferentially spaced axial bores therethrough, said support plates being interconnected by a plurality of brace rods extending through said bores and in operative engagement wtih the core to prevent rotation thereof on the hub.

2. The combination of claim 1 including spacers each surrounding a brace rod and having its opposite ends compressively engaged 'by said pair of support plates, a roller journaled upon each spacer and'revolvably engaging the wall of the associated bore.

3. A rotary piston expansible chamber device comprising a stator having a cylindrical chamber therein including a cylindrical peripheral wall and a pair of annular side walls, a cylindrical core disposed within said cylindrical chamber, a ring piston in said cylindrical chamber having sides slidingly engaging said side walls and dividing said cylindrical chamber into radially spaced outer and inner working chambers disposed respectively adjacent said cylindrical wall and said core, a shaft rotatably journaled coaxially in said cylindrical chamber, eccentric support means fixedly secured to and rotatable with said shaft and supporting and maintaining said ring piston tangent to said core and said peripheral wall, stabilizing means including a pair of cooperating interengaged members fixedly secured one to said stator and the other to said ring piston and confining the latter to translational movement about said core, intake means supplying a fluid to each of said inner and outer working chambers, exhaust means discharging fluid from each of said inner and outer working chambers, radially extending and reciprocable inner and outer partition blades respectively establishing a sealing engagement between said ring piston and said core and cylindrical wall, means applying fluid pressure from the high pressure side of a working chamber to each blade and thereby urging the latter into a pressured sealing engagement with said ring piston, said fluid pressure applying means includes differential areas on said blade, said applied pressure being proportional to the pressure in the associated working chamber and mechanical means assisting said applied fluid pressure in urging said blade towards said ring piston.

4. A rotary piston expansible chamber device comprising a stator having a cylindrical chamber therein including a cylindrical peripheral wall and a pair of annular side Walls, a cylindrical core disposed within said cylindrical chamber, a ring piston in said cylindrical chamber having sides slidingly engaging said side walls and dividing said cylindrical chamber into radially spaced outer and inner working chambers disposed respectively adjacent said cylindrical wall and said core, a shaft rotatably journaled coaxially in said cylindrical chamber, eccentric support means fixedly secured to and rotatable with said shaft and supporting and maintaining said ring piston tangent to said core and said peripheral wall, stabilizing means including a pair of cooperating interengaged members fixedly secured one to said stator and the other to said ring piston and confining the latter to translational movement about said core, intake means supplying a fluid to each of said inner and outer working chambers, exhaust means discharging fluid from each of said inner and outer working chambers, a radially extending and reciprocable outer partition blade extending across said outer working chamber and having a sealing engagement with both said cylindrical wall and said ring piston, said blade comprising a hollow box-like body open at its top and having a bottom wall, a sealing shoe oscillatably mounted upon said bottom wall and having a sealing surface engaging said ring piston, an exhaust passage means extending through said shoe, body and ring piston and continuously communicating with said inner chamber.

. 5. The combination of claim 4 including mechanical means yieldingly urging said shoe into sealing engagement with said ring piston and means applying fluid pressure from the high pressure side of said outer working chamber to said shoe and aiding said mechanical means in effecting a pressured sealing engagement between said sealing shoe and ring piston which is proportional to the pressure in said outer working chamber.

6. The combination of claim 5 wherein said bottom wall and sealing shoe have complementary semi-cylindrical seating surfaces.

7. A rotary piston expansible chamber device comprising a stator having a chamber therein including a peripheral wall and a pair of annular side walls, a core disposed within said chamber, a ring piston in said chamber having sides slidingly engaging said side walls and dividing said chamber into radially spaced outer and inner working chambers disposed respectively adjacent said peripheral wall and said core, a shaft rotatably journaled coaxially in said chamber, a hub fixed to said shaft rotatably mounting said core concentric to said chamber, eccentric support means fixedly secured to and rotatable with said shafit and supporting and maintaining said ring piston tangent to said core and said peripheral wall, stabilizing means including a pair of cooperating interengaged members fixedly secured one to said stator and the other to said ring piston and confining the latter to translational movement about said core, intake means supplying a fluid to each of said inner and outer working chambers, exhaust means discharging fluid from each of said inner and outer Working chambers, a radially extending :and reciprocable inner partition blade extending across said inner working chamber and having a sealing engagement with both said core and ring piston, said core having a radial slot forming a pressure sealed chamber receiving said blade and having at least one guide bore in .said core intersecting said slot, a blade push rod slidable in said bore and engaging said blade, actuating means engaging said push rod and through the latter urgingthe blade towards sealing engagement with said ring piston;

8. The combination of claim 7 including means applying fluid pressure from the high pressure side of said inner working chamber to said blade and aiding said actuator in effecting a pressured sealing engagement between said blade and said ring piston.

9. The combination of claim 8 wherein said pressure applying means includes passages on the high pressure side of said blade conducting fluid from the inner working chamber to the underside of said blade in said slot, said blade having its outer edge rounded whereby only a portion of the area thereof is exposed to the fluid on the high pressure side of said inner working chamber.

10. A rotary piston expansible chamber device com prising a stator having a cylindrical chamber therein including a cylindrical peripheral wall and a pair of annular side walls, a cylindrical core disposed within said cylindrical chamber, a ring piston in said cylindrical chamber having sides slidingly engaging said side walls and dividing said cylindrical chamber into radially spaced outer and inner working chambers disposed respectively adjacent said cylindrical wall and said core, a shaft rotatably journaled coaxially in said cylindrical chamber, eccentric support means fixedly secured to and rotatable with said shaft and supporting and maintaining said ring piston tangent to said core and said peripheral wall, sta bilizing means including a pair of cooperating interengaged members fixedly secured one to said stator and the other to said ring piston and confining the latter to translational movement about said core, intake means supplying a fluid to each of said inner and outer working chambers, exhaust means discharging fluid from each of said inner and outer working chambers, a radially extending and reciprocable inner partition blade extending across said inner working chamber and having a sealing engagement with both said core and ring piston, said core having a radial slot receiving said blade and having at least one guide bore in said core intersecting said slot, a blade push rod slidable in said bore and engaging said blade, actuating means engaging said push rod and through the latter urging the blade towards sealing engagement with said ring piston, means applying fluid pressure from the high pressure side of said inner working chamber to said blade and aiding said actuator in effecting a pressured sealing engagement between said blade and said ring piston which is proportional to the pressure in said inner working chamber, said pressure applying means including passages on the high pressure side of said blade conducting fluid from the inner working chamber to the underside of said blade in said slot, said blade having its outer edge rounded whereby only a portion of the area thereof is exposed to the fluid 'on the high pressure side of said inner working chamber, and a removable pressure seal in said guide bore preventing escape of pressure from said inner working chamber through said guide bore.

11. A rotary piston expansible chamber device comprising a stator having a chamber therein including a peripheral wall and a pair of annular side walls, a core disposed within said chamber, a ring piston in said chamber having sides slidingly engaging said side walls and dividing said chamber into radially spaced outer and inner working chambers disposed respectively adjacent said peripheral wall and said core, a shaft rotatably journaled coaxially in said chamber, a hub fixed to said shaft rotatably mounting said core concentric to said chamber, eccentric support means fixedly secured to and rotatable with said shaft and supporting and maintaining said ring piston tangent to said core and said peripheral wall, stabilizing means including a pair of cooperating interengaged members fixedly secured one to said stator and the other to said ring piston and confining the latter to translational movement about said core, intake means supplying a fluid to each of said inner and outer working cham-' bers, exhaust means discharging fluids from each of said inner and outer working chambers, said core, ring piston and eccentric support means being disposed for limited axial shifting movement, one of said side walls having a circumferentially extending annular channel radially spaced from the hub, a sealing and wear take-up plate received in said channel and engaging the side of said ring piston, means applying controlled fluid pressure to said channel behind said plate urging the latter against said ring piston to thereby effect axial shifting of said core, ring piston and support means.

12. The combination of claim 11 including means preventing rotation of said plate in said channel and means establishing a seal between said plate and channel.

13. A rotary fluid chamber device comprising, a housing, a core rotatably mounted within said housing to form an annular chamber concentric therewith, a piston assembly rotatably mounted Within the chamber in eccentric relation to the core to form radially inner and outer Working spaces within the chamber, partition means mounted by the core for radial displacement into sealing engagement with the piston assembly and differential pressure means for urging the partition means radially outward of the core into sealing engagement with the piston assembly.

14. The combination of claim 13 including shaft means rotatably mounting the core and the piston assembly in eccentric relation to each other, means for preventing rotation of the core during rotation of the shaft means, and cam means engageable with the partition means for imparting radial displacement thereto in response to said rotation of the shaft means augmenting displacement thereof by the pressure means.

15. The combination of claim 14 wherein said partition means includes a radially outer wiping surface engageable with the piston assembly, a radially inner edge surface engageable by the cam means, and side surfaces having radially outer portions exposed to the inner working space, said pressure means including a pressure chamber enclosed within the core by the piston assembly and passage means formed in one of said side surfaces of the partition means establishing fluid communication between the pressure chamber and the inner Working space for exerting pressure on said inner edge surface of the partition means.

16. The combination of claim 13 wherein said partition means includes a radially outer wiping surface engageable with the piston assembly, a radially inner edge surface, and side surfaces having radially outer portions exposed to the inner Working space, said pressure means including a pressure chamber enclosed within the core by the piston assembly and passage means formed in one of said side surfaces of the partition means establishing fluid communication between the pressure chamber and the inner Working space for exerting pressure on said inner edge surface of the partition means.

References Cited by the Examiner UNITED STATES PATENTS 2,073,101 3/1937 FOX 9156 3,011,694 12/1961 Audemar 230-146 3,025,796 3/1962 Miller 103 126 3,068,795 12/1962 Lauck 103126 95 3,125,032 3/1964 Smith 103 131 FOREIGN PATENTS 623,672 8/1961 Canada. 571,291 8/1945 Great Britain.

DONLEY I STOCKING, Primary Examiner.

SAMUEL LEVINE, MARK NEWMAN, Examiners.

W. L. PREEH, Assistant Examiner. 

1. A ROTARY PISTON EXPANSIBLE CHAMBER DEVICE COMPRISING A STATOR HAVING A CHAMBER THEREIN INCLUDING A PERIPHERAL WALL AND A PAIR OF ANNULAR SIDE WALLS, A CORE DISPOSED WITHIN SAID CHAMBER, A RING PISTON IN SAID CHAMBER HAVING SIDES SLIDINGLY ENGAGING SAID SIDE WALLS AND DIVIDING SAID CHAMBER INTO RADIALLY SPACED OUTER AND INNER WORKING CHAMBERS DISPOSED RESPECTIVELY ADJACENT SAID PERIPHERAL WALL AND SAID CORE, A SHAFT ROTATABLY JOURNALED COAXIALLY IN SAID CHAMBER, A HUB FIXED TO SAID SHAFT ROTATABLY MOUNTING SAID CORE CONCENTRIC TO SAID CHAMBER, ECCENTRIC SUPPORT MEANS FIXEDLY SECURED TO AND ROTATABLE WITH SAID SHAFT AND SUPPORTING AND MAINTAINING SAID RING PISTON TANGENT TO SAID CORE AND SAID PERIPHERAL WALL, STABILIZING MEANS INCLUDING A PAIR OF COOPERATING INTERENGAGED MEMBERS FIXEDLY SECURED ONE TO SAID STATOR AND THE OTHER TO SAID RING PISTON AND CONFINING THE LATTER TO TRANSLATIONAL MOVEMENT ABOUT SAID CORE, INTAKE MEANS SUPPLYING A FLUID TO EACH OF SAID INNER AND OUTER WORKING CHAMBERS, EXHAUST MEANS DISCHARGING FLUID FROM EACH OF SAID INNER AND OUTER WORKING CHAMBERS, SAID RING PISTON COMPRISING A CYLINDRICAL RIM AND A PAIR OF SUPPORT PLATES EACH SECURED TO SAID RIM AND JOURNALED UPON SAID ECCENTRIC SUPPORT MEANS, SAID CORE HAVING A PLURALITY OF CIRCUMFERENTIALLY SPACED AXIAL BORES THERETHROUGH, SAID SUPPORT PLATES BEING INTERCONNECTED BY A PLURALITY OF BRACE RODS EXTENDING THROUGH SAID BORES AND IN OPERATIVE ENGAGEMENT WITH THE CORE TO PREVENT ROTATION THEREOF ON THE HUB. 